JP2001527195A - Gear shifter for transmission - Google Patents

Abstract

SUMMARY The present invention relates to a control fluid operated gear shifter (118) for coupling at least one stage with components of a transmission (102) rotating at different speeds. One unit in which the valve (4, 5, 6, 7), shift cylinder (1), piston (2) and shift member (2A) are integrated for each stage is provided. The gear shifter (118) is operated by an electrically controlled pulse-operated two-way valve (4, 5, 6, 7) and is connected to the position measuring device (3). To the direction valves (4, 5, 6, 7). The signal controls the two-way valve (4, 5, 6, 7) according to the position of the piston (2) with respect to the shift cylinder (1) detected by the position measuring device (3).

Description

DETAILED DESCRIPTION OF THE INVENTION

The present invention relates to a gear shifter for a multi-stage transmission based on the generic concept of claim 1.

[0002] Underlying the invention is the task of presenting a gear shifter that allows variable synchronization times and quick shift times.

This problem is solved by a gear shifter having the features of claim 1. Embodiments are the subject of the dependent claims.

It is proposed to provide one unit in which the valve, the shift cylinder, the piston and the shift member are integrated for each stage of the multi-stage transmission.

[0005] A pulse operated two-way valve is used as the actuating valve. In that case, a position measuring device is used which indicates the current position of the piston relative to the shift cylinder.

[0006] It is thereby possible to adapt the shifting force and the shifting time when inserting the gear into the torque transmitting connection. Adaptation means that a higher frequency acts on the valve, especially when the connection is made, than when it is disconnected.

In another advantageous embodiment, the pulse frequency of the two-way valve when shifting on level ground is:
It is set to be different from the pulse frequency in the case of shifting on uneven terrain, ie uphill and downhill.

[0008] In another advantageous embodiment, the pulse frequency of the two-way valve is designed to be able to be controlled as a function of the vehicle weight.

In a preferred embodiment, the operation of the pulse-operated valve takes place at a voltage several times the rated voltage of the valve.

[0010] Preferably, the position measuring device is provided inside the shift cylinder. The position measuring device can also be provided at a position outside the shift cylinder, at which position the position measuring device is connected to the movable part of the unit.

[0011] In another advantageous embodiment, the piston of the shift unit is arranged on a piston rod, on which it can be moved axially. The pistons of a plurality of stages of shift units can be provided on this single piston rod without interfering with each other. It is preferable that the units of each stage are arranged in one row.

In a further preferred embodiment, each shift unit belongs to one stage and a plurality of shift units are combined in one component. This part can be assembled separately from the transmission and then adapted and attached to the transmission as a single unit. This allows the complete set of gear shifters to be manufactured and tested independently of the type of transmission.

[0013] In an advantageous embodiment, the gear shifter has a stop which cushions the collision contact of the piston with the edge of the shift cylinder. This stop can be provided inside the shift cylinder, or it can be provided externally at the part of the shift unit which is connected to the piston.

[0014] In contrast to known gear shifters, all gear shifters are immediately adjacent to the stage.

[0015] Preferably, one stage consists of two gears which are juxtaposed in the transmission and can be connected to a torque transmission alternately. However, it is also possible for one gear to consist of only one gear connected to the torque transmission, for example, if two opposite gears do not have to be connected when shifting to a reverse gear ratio.

By providing a compact unit, there is no need for a coupling member between the shift member, preferably a shift fork or a shift rocker, and the shift cylinder and the shift piston. Such a coupling member is a shift rod, generally made of steel, as described above, and contributes significantly to the overall weight of the transmission. The response time between the command to initiate the shift and the movement of the shift member is significantly reduced by the elimination of the heavy shift rod to be moved.

The present invention will be described in detail with reference to the drawings.

FIG. 1 shows a schematic diagram of a transmission 102 of a vehicle, not shown here. Transmission 10
2 is a clutch bell housing 104, a main transmission 106, and an auxiliary transmission 108
And a drive shaft 110 and a driven shaft 112 having an output flange 114. The main transmission 106 is provided with components 116. Part 116 has three separate gear shifters 118, 120 and 122 in the configuration shown. A shift fork 124 of a gear shifter 118 shown as an example is engaged with a slide sleeve 126. The slide sleeve 126 is axially movable along a shaft 128 and is non-rotatably secured to the shaft 128. The sliding sleeve 126 is connected to the gear 130 or 132 by moving to form a torque transmission path. The gear shifters 118, 120 and 122 are connected via a wire 134 to a control device 136, for example a transmission computer or a main computer of the motor vehicle. Further, the gear shifters 118, 120 and 122 are connected to a pressure source 138 of the working fluid via a pipe 140.

FIG. 2 shows a partial view of the housing of the transmission 102 in which the gear shifters 118, 120 and 122 are combined into one part 116. The part 116 is a connecting member 1
It is fixed to the transmission 102 by 44. The gear shifters 118, 120 and 122 have a pipe 140 for supplying a working fluid and an electric wire 1 connected to a control device 136.
34 are connected.

FIG. 3 is a longitudinal sectional view showing the operation principle of the gear shifter 118 of the automatic vehicle transmission having the position measuring device and the pulse-operated directional control valve. The gear shifter 118
It has a shift cylinder 1 and a shift piston 2 composed of two cylinder portions 1A and 1B.

By forming the shift cylinder 1 with two separate cylinder parts 1A and 1B, the driven mass can be greatly reduced.

The shift piston 2, which is formed as a shift member in the embodiment shown, moves between the fixed cylinder parts 1 A and 1 B.

In this case, since the shift piston 2 has the shift fork 2A as an integral component, no coupling member is required between the shift piston 2 and another shift member, for example, the shift fork 2A or the shift rocker. It is. Thus, the connection between the shift piston 2 and the shift fork 2A is formed firmly and at the shortest distance.

Although not shown, the cylinder portions 1A and 1B and the shift fork 2A
Can also be configured so that the cylinder parts 1A and 1B make a relative movement with respect to the shift piston 2.

Since the design is extremely advantageous, that is, based on the structure of the split type shift cylinder 1 composed of the two cylinder portions 1A and 1B, the cylinder portions 1A and 1B can be used as a shift member, so that various speed changes can be made. Machine design is possible.

As shown in FIG. 3, for detecting the position of the shift piston 2 in the shift cylinder 1 or between the cylinder parts 1 A and 1 B, a position measuring device 3 connected to a control device 136, for example a guidance position A sensor is mounted parallel to the shift axis of the shift piston 2. The control device 136 transfers an electronic control signal to the pulse operation valves 4, 5, 6, and 7 according to the position of the shift piston 2 detected by the guidance position sensor.

The shift piston 2 has a guide shoulder 2B, and each cylinder part 1A and 1B
The shift piston 2 is guided by this guide shoulder in the turning groove 8 formed in the groove. Both the cylinder parts 1A and 1B and the shift piston 2 are arranged around a bar 9. The bar 9 passes through the cylinder portions 1A and 1B and the center of the shift piston 2 in the direction of movement of the shift piston 2.

The cylinder portions 1 A and 1 B of the shift cylinder 1 and the shift piston 2 are
In particular, this allows a single row of shift cylinders to be easily arranged in a small number of mounting locations, especially since reduced component costs and simple assembly provide a decisive cost advantage. It is convenient. In principle, the controls for all gear shifters of the transmission can be mounted on this bar 9.

Referring to FIG. 3, the cylinder portions 1A and 1B are pre-assembled and fixed to the bar 9 by fixing. However, depending on the dimensional tolerance of the transmission, the cylinder portions 1A and 1B can be fixed in the mounted state.

To switch the shift piston 2 in the shift cylinder 1, an external pressure source 13
From 8 via a pressure tube 10 or 11 a pneumatic or hydraulic working medium is sent to a gear shifter. Two two-way solenoid valves 4, 5 and 6, 7 for the pressure lines 10 and 11, respectively.
These valves are arranged so that the shift piston 2 moves at a speed corresponding to the optimum speed at this stroke position, which is empirically or simulated.
It controls the flow of the working medium through the pressure tubes 10 and 11. The manner of valve control can be adapted according to the mass to be shifted based on the characteristics of the transmission.

The pulse operated valves 4, 5, 6 and 7 are designed to operate continuously at 4 volts, but in this case they are operated with 24 volt pulses. Pulse operation valves 4, 5,
By driving 6 and 7 with strong current pulses, the valve responds very quickly.
In that case, the pulse operation valves 4, 5, 6 and 7 are controlled by the control device 136 according to the position of the shift piston 2 in the shift cylinder 1 detected by the position measuring device 3. Various electric pulses are generated according to the position of the shift piston 2,
5, 6 and 7, wherein the pulse-operated valve is opened at a predetermined high pulse frequency and closed at a predetermined low pulse frequency. In this way, the flow of the working medium that moves the shift piston 2 in the shift cylinder 1 and the speed of the shift piston 2 in the shift cylinder 1 during the shift operation are changed. The control of the pulse-operated valves 4, 5, 6 and 7 is in that case designed such that all pulse-operated valves operate individually or in opposition or together.
In this way, different speeds of the shift piston and thus different dynamic forces are obtained.

In this way, the shift piston is moved at the highest possible pressure during the entire shift stroke up to the start of synchronization of the transmission and, after the end of the synchronization phase, is shifted at a lower speed to the end position. The piston speed is varied by two pulse-operated two-way valves each.

Next, the principle of the shift process will be described to clarify the function of the gear shifter.

In the shifting process, when the working medium is sent to the gear shifter through the pipe 10, the pulse operation valve 5 having the function of the inflow valve is opened, and the pulse operation valve 4 formed as the outflow valve is closed. Thus, the working medium passes through the cylinder portion 1A via the pipe line 10 and reaches the working chamber 12 of the shift piston 2, and the shift piston 2 is moved from the stop surface 13 of the cylinder portion 1A to the stop of the cylinder portion 1B facing the stop surface 13. Move in the direction of surface 14.

When the synchronizing phase has started in the transmission, the shift piston 2 remains in the locked position just before hitting the stop surface 14. At this time, since the working medium is continuously supplied through the pipe 10, the effect of the pressure on the shift piston 2 is greatly increased.

The part of the working chamber 12 of the shift piston which is in the direction of movement of the shift piston 2 is relieved during the entire shift operation by the pressure line 11 and the open pulse-operated valve 6 designed as an outlet valve. The pulse control valve 7 for supplying the working medium is then closed.

At the end of the synchronization process, the shift piston 2 is unlocked, so that the shift piston 2 is again moved in the direction of the end position of the stop surface 14 at a high speed due to the high charging pressure during the synchronization process. At that time, the position of the shift piston 2 is detected by the position measuring device 3. The position measuring device 3 controls the pulse operated valves 6 and 7 with electric pulses so that the pulse operated valve 6 for discharging air is closed. As a result, the movement of the shift piston 2 in the last short section up to the stop surface 14 sharply decreases due to the so-called cushion action of the working medium. The pressure supply via the pulse-operated valve 5 of the pressure line 10 is regulated by closing the supply valve 5 during or shortly after the shift piston 2 is stopped during the synchronization phase of the transmission. Regardless of the cushioning of the working medium between the shift piston 2 and the stop surface 14, the shift piston 2 is
Immediately before colliding contact with the valve, the pulse operating valve 6 is switched to the open position by the position measuring device 3, whereby the working medium between the shift piston 2 and the stop surface 14 can escape from the pressure pipe 11, Does not rebound when hit against the stop surface 14.

In the case of reverse operation, the same shift operation is performed in the reverse direction, the pulse operated valves 5 and 6 are closed, and the gear shifter is supplied with pressure by the pressure pipe 11 and the opened pulse operated valve 7, The pressure is released by the opened pulse operation valve 4 and the pressure pipe 10.

In the proposed gear shifter, the synchronization time can be changed by electronic control of the pulse operation valve. In this way, the synchronization operation is performed differently for the shift on the flat ground and the shift on the downhill and the uphill. When shifting on level ground, the synchronizer can be operated very carefully. On the downhill, the synchronizer works with a high pulse frequency,
The maximum load is utilized, so that a shift time reduction important for safety can be achieved. The variable shift or synchronization force optimizes the shift speed.

If the vehicle is further provided with a calculation of the vehicle weight, the result of this calculation can be incorporated into the control of the pulse frequency. In this way, the synchronization time can be adapted according to the vehicle weight, and a further optimization of the shift time and a careful handling of the synchronization action can be obtained.

In order to avoid shifting in the case of tooth-to-teeth collisions of the coupled gearing, monitoring of such conditions can be provided. When such a condition is recognized, the synchronizing action provides a resistive torque, and the synchronizing force is minimized to eliminate tooth-to-teeth collision.

When controlling the valve, care must be taken not to overload the valve.
Overload can be caused by successive pulses or too short a pulse interval.

[Brief description of the drawings]

FIG. 1 is a diagram of a transmission having a gear shifter.

FIG. 2 is a diagram of an array of gear shifters.

FIG. 3 is a diagram of a gear shifter.

[Explanation of symbols]

 DESCRIPTION OF SYMBOLS 1 Shift cylinder 1A Cylinder part 1B Cylinder part 2 Shift piston 2A Shift fork 2B Guide shoulder 3 Position measuring device 4 Pulse operated valve 5 Pulse operated valve 6 Pulse operated valve 7 Pulse operated valve 8 Turning groove 9 Guide bar 10 Pressure pipe 11 Pressure Pipe 12 Working chamber of shift piston 13 Stop surface 14 Stop surface 102 Transmission 104 Clutch / bell housing 106 Main transmission 108 Auxiliary transmission 110 Drive shaft 112 Follower shaft 114 Output flange 116 Gear shifter 118 Gear shifter 120 Gear shifter 122 Gear shifter 124 Shift fork 126 Slide sleeve 128 Shaft 130 Gear 132 Gear 134 Electric wire 136 Control device 138 Pressure source 140 Pipe line 144 Coupling member

[Procedural Amendment] Submission of translation of Article 34 Amendment of the Patent Cooperation Treaty

[Submission date] December 16, 1999 (Dec. 16, 1999)

[Procedure amendment 1]

[Document name to be amended] Statement

[Correction target item name] Claims

[Correction method] Change

[Correction contents]

[Claims]

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Claims (18)

[Claims] A gear shifter (118) operated by a control fluid for connecting parts of a transmission (102) rotating at different rotational speeds and at least one stage, wherein a valve (4, 5) is provided for each stage. , 6, 7), a shift cylinder (1), a piston (2) and a shift member (2A) are integrated into one unit, and the gear shifter (1
18) is operated by an electrically controlled pulse operated two-way valve (4, 5, 6, 7);
The gear shifter (118) is connected to the position measuring device (3), and the signal of the position measuring device (3) is transmitted to the two-way valve (4, 5, 6, 7) and detected by the position measuring device (3). Depending on the position of the piston (2) with respect to the shift cylinder (1), the two-way valve (4, 5
, 6, 7) for controlling the gear shifter (118). 2. The pulse frequency of the two-way valve (4, 5, 6, 7) when the gear shifter (118) is closed is higher than when the gear shifter (118) is open. 1
(118). 3. The pulse frequency of a two-way valve (4, 5, 6, 7) when shifting on level ground is different from the pulse frequency when shifting on uneven roads.
Or the gear shifter (118) according to 2. 4. The pulse frequency of the two-way valve (4, 5, 6, 7) when shifting on level ground is lower than the pulse frequency when shifting on uneven roads.
(118). 5. The gear shifter according to claim 1, wherein the pulse frequency of the two-way valve (4, 5, 6, 7) can be controlled according to the vehicle weight. 1
18). 6. The gear shifter (118) according to claim 1, wherein a voltage corresponding to several times the rated voltage of the valve acts on the valve (4, 5, 6, 7). . 7. The gear shifter (118) according to claim 1, wherein the position measuring device (3) is arranged inside the shift cylinder (1). 8. The gear shifter (118) according to claim 1, wherein the position measuring device (3) is arranged outside the shift cylinder (1). 9. The method according to claim 1, wherein the piston is arranged on the piston rod and is axially movable on the piston rod. The gear shifter (118) according to any one of the first to third aspects. 10. A method according to claim 1, wherein a plurality of gear shifters are provided for a plurality of stages, and one gear shifter is assigned to each stage. The gear shifter (118) according to any one of the preceding claims. 11. The gear shifter (118) according to claim 10, wherein a plurality of gear shifters (118, 120, 122) are arranged in a row. 12. The gear shifter according to claim 10, wherein the pistons (2) of the plurality of gear shifters (118, 120, 122) are arranged on a common piston rod (9). (118). 13. The device according to claim 10, wherein a plurality of gear shifters (118, 120, 122) are provided on separate components (116) that can be connected to the transmission (102). Gear shifter (118) according to any one of the preceding claims. 14. The gear shifter (118) according to claim 13, characterized in that the function of the part (116) can be adjusted and tested independently of the transmission (102). 15. The gear shifter according to claim 1, wherein a stop is provided for damping the abutment of the piston (2) against the edge of the shift cylinder (1). (118). 16. The shift cylinder (1), wherein the stop is provided inside the shift cylinder (1).
The gear shifter (118) according to claim 15, wherein: 17. The stop, wherein the stop is provided outside the shift cylinder (1).
The gear shifter (118) according to claim 15, wherein: 18. A tooth-to-tooth collision discriminating means is provided, wherein a reduction in synchronizing force provides a resistive torque, whereby tooth-to-tooth collision is eliminated. The gear shifter (118) according to claim 1.